Rotating basket condensing apparatus



Feb. 22, 1966 J H. DAVIDS ROTATING BASKET GONDENSING APPARATUS 4 Sheets-Sheet 1 Filed April 29, 1965 INVENTOR. JOHN H. DAVIDS Feb. 22, 1966 J. H. DAVIDS 3,236,229

ROTATING BASKET CONDENSING APPARATUS Filed April 29, 1963 4 Sheets-Sheet 2 INVENTOR. JOHN H DAVIDS BY Eadu, (BMW @AmMe/y, Mmadz gttgls.

Feb. 22, 1966 J. H. DAVIDS ROTATING BASKET CONDENSING APPARATUS 4 Sheets-Sheet 5 Filed April 29, 1963 Feb. 22, 1966 J. H. DAVlDS ROTATING BASKET CONDENSING APPARATUS 4 Sheets-Sheet 4 Filed April 29, 1963 INVENTOR. JOHN H DAWDS 52M, EKG/(110% United States Patent 3 236,229 ROTATEQG BASKET CONDENSING APPARATUS John Hans Davids, Beloit, Wis., assignor to Desalination Plants (Developers of Zarchin Process) Limited, Tel

Aviv, Israel, a company of Israel Filed Apr. 29, 1963, Ser. No. 276,507 22 Claims. (Cl. 126-3435) This invention relates to new and improved means and methods for separating a solvent in substantially pure form from a solution, and is more particularly directed to new and improved means and methods for condensing vapor.

Heretofore, difficulty has been encountered in the design of apparatus for condensing large volumes of vapor efliciently, particularly when the vapor is to be condensed at the surface of the ice, when in contact with vapor, and,

thus, the total evaporative surface of the ice, when large quantities of ice are to be melted, presents a space problem, i.e., the ice must be spread out to provide a large evaporating surface. These problems are particularly critical when the large volumes of vapor and ice are to be condensed and melted, respectively, on a continuous basis, such requirement being presented in such systems as desalination systems for producing fresh or potable water from sea or brackish water.

With the present invention, the above-mentioned problems and difliculties and others are substantially overcome by the provision of apparatus for condensing vapor and melting ice which includes a condensing chamber in which is disposed rotatable means for receiving and distributing the ice in the chamber whereby the ice may be introduced into the chamber from a fixed or single location, the ice moving down an inclined surface of said means and means for supplying vapor in contact with the ice so moving to condense the vapor and melt the ice, the fluid of the ice and condensate fluid of the vapor flowing through an outlet from the chamber.

It is, therefore, an object of the present invention to provide new and improved condensing apparatus for condensing vapor.

It is another object of the present invention to provide new and improved condensing apparatus for condensing vapor and melting ice.

Still another object of the present invention is to provide new and improved condensing apparatus for condensing vapor and melting ice which includes rotatable means for receiving the ice, and means for flowing vapor into contact with the ice to condense the vapor and melt the ice.

A further object of the present invention is to provide new and improved condensing apparatus including a condensing chamber having a fixed inlet for supplying ice into the chamber and onto rotatable means in the chamher, and an inlet for supplying vapor into the chamber for contact with the ice on said rotating means to condense the vapor and melt the ice.

A still further object of the present invention is to provide new and improved condensing apparatus including a single inlet for supplying ice into the chamber and onto rotating means, and an inlet for supplying vapor into the chamber and into Contact with the ice on said rotating means to condense the vapor and to melt the ice.

ice

Another object of the present invention is to provide new and improved condensing apparatus including 21 I0- tatable member having an inclined surface for receiving ice, and means for flowing vapor into contact with the ice to condense the vapor and to melt the ice.

Still another object of the present invention is to provide new and improved condensing apparatus for condensing vapor and melting ice including a rotatable member in the condensing chamber having an inclined surface for receiving ice, means for delaying movement of ice along said inclined surface, and means for flowing vapor into contact with the ice to condense the vapor and to melt the ice.

A further object of the present invention is to provide new and improved condensing apparatus including totatable means for receiving ice, means for rotating the rotatable means, and means for flowing vapor into contact with the ice to condense the vapor and to melt the ice.

A still further object of the present invention is to provide new and improved condensing apparatus including a rotatable, hollow frusto-conical member having an inner inclined and ice receiving surface, means for supplying ice onto said surface, means for temporarily interrupting movement of ice along said surface, and means for flowing vapor into contact with the ice to condense the vapor and to melt the ice.

Another object of the present invention is to provide new and improved condensing apparatus for condensing vapor including a rotatable, hollow frusto-conical member having an inner ice receiving chamber defined by the inner inclined surface of the ice receiving chamber, a fixed inlet for supplying ice onto said surface, and means for flowing vapor into contact with the ice to condense the vapor and to melt the ice.

A further object of the present invention is to provide new and improved condensing chamber apparatus for condensing vapor and melting ice which is compact and simple in construction and efficient and comparably highspeed in operation.

Another object of the present invention is to provide new and improved methods for condensing vapor and melting ice.

These and other objects, features and advantages of the present invention will become readily apparent from a careful consideration of the following detailed description, when considered in conjunction with the accompanying drawings illustrating a preferred embodiment of the present invention, wherein like reference numerals and characters refer to like and corresponding parts throughout the several views, and wherein:

FIG. 1 is a view in partial section illustrating apparatus for condensing vapor and melting ice constructed in accordance with the present invention and as employed in conjunction with a flash freezing chamber of a desalination system;

FIG. 2 is an enlarged fragmentary view in vertical section illustrating the details of the condensing chamber of FIG. 1;

FIG. 3 is a top view in elevation of the condensing apparatus of FIG. 2 taken along line 3-3 of FIG. 2 and illustrating the details of means employed to receive ice and delay movement of ice on said means;

FIG. 4 is an enlarged view in partial section taken along line 44 of FIG. 2;

FIG. 5 is an enlarged view in partial section taken along line 5-5 of FIG. 2;

FIG. 6 is a view in perspective of means employed to delay movement of ice along the rotatable means of FIG. 2, and

FIG. 7 is a view taken along line 77 of FIG. 2.

J General description of the system Although the present invention has a variety of applications, a suitable embodiment thereof employed in a de sal-ination system for producing fresh or potable water from sea water appears in FIG. 1.

A desalination system, with which the condensing apparatus 18 of the resent invention is eminently suitable for use, includes an evaporating chamber and a compressor, 54 disposed in the upper central portion of the condensing chamber 18 as appears in FIG. 1 and the general arrangement of a suitable desalination system, such as the system disclosed in US. application, Serial No. 103,114, filed April 14, 1961, now abandoned, the disclosure. of which is hereby incorporated herein by reference, will be first briefly described:

Generally, sea water, which is at ambient temperature, and which has been filtered to remove floating material and other solids is brought into the desalination system and passes through a deaerator (not shown) where dissolved gas is removed from the sea water. The sea water is then delivered under pressure to heat exchange means (not shown), where the incoming sea water is placedin heat-exchange relationship with the potable water final product and. concentrated brine being withdrawn from the system.

The sea water entering the system will be normally at ambient temperature, such as for example 77 F. and normally contains about 3.5% by weight of salt.

The sea water leaving the heat exchange means will be at a temperature of approximately 302 F. and is delivered into an. evaporating chamber 20 which may be an evaporating chamber, such as the chamber disclosed in US. application, Serial No. 103,112, the disclosure of which is hereby incorporated herein by reference. The sea water enters the evaporating chamber and thereafter flows downwardly insuch a manner that the incoming sea Water has a large surface exposure for evaporation.

The interior of the evaporating chamber 20 is maintained at a low pressure, approximately 3.2 mm. Hg (millimeters of mercury), by a vacuum pump (not shown)- Due tothe fact that the interior of the evaporating chamber is at such low pressure sea water will flash-evaporate therein. At the freezing temperature of sea water, the heat. of vaporization is approximately 1074 B.t.u. per pound and the heat of fusion of ice is about 144 B.t.u., per pound. As vapor is produced by evaporation, heat is removed from the. remaining liquid and ice is formed. therein. Due to the diiferences in heat of vaporization and heat of fusion, approximately 7 /2 pounds of ice will be produced for each pound of water vapor. The ice so produced is substantially pure water ice with no appreciable amount of salt contained therein. When continuous operation is established, the temperature within the evaporating chamber will be approximately 24.8 F. The vapor formed will be pure water vapor. Thus, upon removal of the pure water from the incoming sea water by the vaporizing and freezing, the remaining sea water becomes a more concentrated salt solution.

While theoretically in excess of 75% pure water by weight could be removed in the form of vapor and ice, we have found that removing approximately 50% by weight of pure Water is in the range of greatest efficiency; thus, if ap roximately 50%v of the water is removed as vapor and ice, the, remaining brine solution will consist of approximately 7% by weight of salt.

The evaporation of water, with the consequent formation of vapor and ice, is a function of time since heat must be transferred, and also the rate of evaporation is proportional to surface area. In order to have the sea water remain in the evaporating chamber for a sufficient period of time and to offer large surface exposure of the sea water, distributor means (not shown) may be disposed within evaporating chamber 20.

The brine, with the ice crystals therein, is withdrawn from the bottom of evaporating chamber 20, and this mixture has a temperature of approximately 24.8 F. The mixture is delivered to a separator washer or counterwasher, in which the ice is separated from the concentrated brine and the ice is washed free of salt adhering to the surface of the ice crystals. The ice-brine mixture enters the lower end of the separator-washer under pressure and the column of the separator-washer becomes essentially full of ice crystals. The pressure exerted by the entrance of the brine at the bottom of the counterwasher forces the cylinder of ice packed therein upwardly, and this brine forces its way through the ice pack, out through screen means. A pump removes the brine from around the lower end of the counterwasher. The pressure drop, created by forcing brine through the ice pack within the column, exerts a force on the column of packed ice moving it upwardly. Thus, the ice column within the counterwasher continuously moves upwardly. At the upper end thereof is a motor-driven scraper or wiper which Wipes off the top of the upwardly moving column of ice and delivers the ice into a trough. Spray heads are provided at the top of the counterwasher for spraying sweet water onto the top of the porous column of ice, which water runs downwardly over the advancing column of ice to wash away any adhering brine on the surface or in the interstices of the ice.

Sweet water is added to the ice in the trough so as to produce a solution of sweet water and ice suspended therein which can be pumped.

By supplying sweet water to the ice to provide a liquid with the ice suspended therein, the resulting material may be more readily handled, and the liquor prevents the breaking of the vacuum within the vacuum chamber. An ice sweet water pump is employed for delivering the material to a conduit 50 connected to an inlet 156 of a condensing chamber apparatus constructed in accordance with the present invention.

A compressor 54, which is a radial compressor, is positioned within the upper end of condensing chamber and has an axial intake opening 56 in communication with evaporating chamber 20 and a circular outlet 58 communicating with the open end of the condensing chamber.

Vapor formed in evaporating chamber 20 is drawn into central inlet 56 of compressor 54 and delivered radially outward into the condensing chamber through the outlet 58. The vapor is thus compressed and compressor 54 maintains the condensing chamber at a pressure of approximately 4.6 mm. Hg. The vapor delivered by the compressor into the condensing chamber passes downwardly into contact with the ice disposed in the chamber and simultaneously causes the vapor to condense and ice to melt. The sweet water thus produced is withdrawn from the lower end of the condensing chamber which may deliver a portion of the sweet water back to counterwasher for ice washing and for mixing with the ice. The majority of the sweet water product from the con.- densing chamber passes to the heat exchange means.

One of the greatest difliculties encountered in prior art vacuum freezing systems is their inability to efiiciently and economically handle and transport the large. volumes of vapor that exist for any system producing a meaningful amount of sweet Water, particularly when it is recognized that we are dealing with such low pressures that approximately 4,500 cubic feet of vapor at these pressures is required to provide one pound of water vapor. Normally, to move any such large volume, a multi-stage axial compressor would be required and the cost of the impellers and housings Without considering the conduit size and expense would make the system uneconomical.

Additionally, by positioning the compressor within one of the chambers, the pressure. differential across the shrouds is so slight that a very inexpensive shrouding may be used on the compressor. In essence, the housing of the vessel into which the compressor discharges is the real structural support housing of the compressor.

Likewise, with the arrangement proposed, the compressor serves as a self-regulator upon the system since the amount of vapor that can be handled by the compressor will control the rate at which vapor is formed by vaporization and the rate at which it is condensed.

Ideally, the vapor should be delivered to the condensing chamber at saturation conditions of pressure and temperature so that the vapor will condense on the 32 F. ice and the ice will take out of the vapor 1,074 Btu. per pound of vapor condensed and thereby cause the 32 F. ice to melt by each pound absorbing 144 B.t.u.

The motor for driving the compressor 54 is located outside of the condensing chamber so that it will not introduce heat into the system.

As previously described, the final product, potable water, is delivered from the condensing chamber to the heat exchange means and is at a temperature of approximately 32 F. The concentrated brine which has been separated from the ice in the counterwasher is delivered to the heat exchange means and is at a temperature of approximately 24.8 F.

The purpose of the heat exchange means is to cool the incoming sea water to the maximum extent possible by withdrawing heat therefrom and delivering it to the cold brine and sweet water produced, and it is important that the sea water be cooled as efliciently as possible. With employment of heat exchange means, approach tem peratures of about 2 F. have been achieved and, thus, sea waterentering the system is at about 30.2 F.

The sweet water, as it leaves the heat exchange means is the principal product of this system and is delivered to storage tank means from which it may be withdrawn for use. The warmed concentrated brine, as it leaves the heat exchange means is delivered to a waste outlet for return to the sea or for other use or disposal.

It should be noted that a higher pressure is necessary in the condensing chamber than in the evaporating chamber because the vapor pressure of the freezing brine is lower than the vapor pressure of the ice water mixture at 32 F. The vapor pressure of brine of 7% by weight salinity at 24.8 F. is about 3.2 mm. Hg, while the vapor pressure of ice water mixture at 32 F. is about 4.6 mm. Hg. The compressor maintains this condition.

It has been found advisable to recirculate a portion of the cold brine in order to prevent ice from building up within the evaporating chamber and thereby plugging the system and stopping continuous operation. Thus, a portion of the cold brine taken from the counterwasher is delivered into the evaporating chamber. Likewise, a portion of the cold concentrated brine is delivered to the incoming cold sea water. Thus, cold concentrated brine is mixed with the incoming sea water and passes through the evaporating chamber 20 and this mixture is joined in the chamber by concentrated brine. This introduction of concentrated brine with the sea water does not interfere adversely with the evaporation and formation of vapor and ice. In addition, small ice crystals escaping from the drainage area of the counterwasher are thus reintroduced into the system to promote crystallization. Also, the greatest amount of ice is present in the icebrine mixture at the bottom of the evaporating chamber and there is a tendency for ice build-up at that point. However, the introduction of additional brine increases the fluidity of the total mixture and also has a flushing action at the bottom of the evaporating chamber.

In any commercially successful desalination system, relatively large volumes of potable water must be produced and, while this may be effected by building larger and larger equipment, again, within shadow of commercial unacceptance due to high cost, the size of the equipment must be reasonable. With the system, schematically shown in FIG. 1, it is contemplated that approximately 60,000 gallons of potable Water per 24-hour day would be produced. Rather than attempt to increase the size of the equipment and thereby add to its expense out of proportion to gain, it is contemplated that when larger production of potable water is required, which will normally be the case, separate but parallel systems will be installed and operated to supply additional requirements.

By referring to FIG. 1, it will be seen that compressor 54 is disposed within the outer housing of the condensingevaporating chambers. In the particular embodiment, the compressor is disposed immediately below the cover 60 of the condensing chamber and above the cylindrical wall of the evaporating chamber 20. The compressor is actually supported by this cover 60 and comprises a housing or shroud 62, having a top housing 64 and a lower housing or shroud 66, which are secured together but spaced around the periphery of the compressor by attachment means 68. Bottom shroud 66 is provided with the previously mentioned central inlet 56, and the annular space between the top and bottom shroud-s, extending completely around the compressor, provides the circular outlet 58 previously identified. Shrouds 64 and 66 are so sealed to the walls of the chambers that the only communication between the chambers is through central inlet 56, the interior of the compressor, and circular outlet 58. Mounted within housing 64 is a rotating impeller 70 and it is important to note that this impeller is bearinged within and supported by the top cover 60 of condensing chamber 18. The housing 64 does not journal or support the impeller 70 and the housing is a lightweight shroud fully supported by cover 60, which with the other walls is the effective support and heavy-duty housing for the compressor. As seen in the drawings, the shroud or housing 64 is of thin, light construction. The impeller 70 comprises a plurality of radially extending blades 72 and central hub 74 and is rotated by a motor 78 within housing 64. It must be appreciated that in order to move the volume of vapor required, this compressor is large and rotates at a relatively high speed. For example, the diameter of impeller 7 0 will be approximately 7 feet and the speed of rotation will be 3,600 r.p.m. For such speed of rotation and size of impeller, it is therefore, most important that a strong and yet light weight rotor be provided. Since the cover 60 is a substantial structural member, it is able to afford the necessary support and provide a primary housing while the actual shroud or covering for the impeller is of relatively light material. In essence, the chamber into which the compressor is discharging serves here as the housing for tthe compressor and support for the drive.

While the system is operating and the compressor is rotating, vapor formed within evaporating chamber '20 is drawn into central inlet 56, and is moved by rotating blades 72 radially outward at progressively increasing pressure for ultimate discharge through circular outlet 58 into the condensing chamber. In other words, the compressor affords a direct radial path for movement of the vapor. Important also is the fact that vapor will be drawn into the compressor throughout the entire area of central inlet opening 56 and discharged throughout the entire area of circular outlet 58. Thus, vapor will be delivered around the entire annular area of the condensing chamber for movement into contact with the ice that has been spread out within substantially the entire area of the condensing chamber. With this concentric chamber and compressor arrangement, vapor will move from all points of discharge from the compressor in a spiral path downwardly through the condensing chamber maintaining the high velocity imparted to the vapor by the compressor. Since condensation is a function of surface contact and velocity of relative flow, this is, of course, advan tageous. The advantages of the arrangement with regard to size and cost of equipment must be emphasized and appreciated and this close-coupled relationship of the compressor and chambers accomplishes these advantages. If a conventional volute type casing for a compressor were utilized, its diameter would be about 14 feet and to convey the volume of vapor contemplated for the type of equipment shown, ducts having diameters of approximately 6 feet would be required. Equipment of this size obviously introduces thermal losses into the system and the cost of the parts and of insulation becomes substantial.

To a large degree vacuum freezing desalination systems have heretofore been penalized because of the failure to provide efficient and economical equipment for and arrangements of the compressor and condensing and evaporating vessels. With the arrangements contemplated in the past to move such a large volume of vapor, one would normally use an axial compressor having several stages. The cost of such a compressor arrangement alone, and certainly When combined with the cost of providing evaporating and melting vessels, would most likely exceed the permissible cost for an entire system for desalination.

Condensing and melting apparatus Referring to FIGS. 2 and 3 which illustrate the details of the condensing and melting apparatus 18, it will be observed that the apparatus 18 defines a condensing and melting chamber, generally indicated by the numeral 102, which is concentric with the vapor flow chamber 20a of the evaporating chamber 20. The chamber 102 is defined by an inner cylindrical wall 104, an outer wall 106 and a bottom wall 108. It will also be observed that the chamher 102 has an open top 110 which communicates with the outlet 58 of the compressor 54 for supplying vapor from an annular path into the chamber 102, which is a vacuum chamber.

Disposed within the chamber 102 is rotatable means, generally indicated by the numeral 112, which includes a hollow frusto-conic-al member 114 spaced from the walls of the chamber 102. The frusto-conical member 114 defines an inclined surface 116 which tapers from its upper end 118 downwardly and inwardly to its opposite open lower end 120.

A lower perforated hollow frusto-conical ring 121 is mounted to a frusto-conical support member 122 below member 114 and provides drain means for condensate fluid of the vapor and fluid of the ice. The lower end of the member 122 is carried by a bottom rotatable drive ring 124, the operation and description of which will be presented hereinafter.

Concentric with the inner wall 104 of the chamber 102 is a sleeve 126 which is carried by the ring 124 and which acts as a support for the frusto-conical member 114.

The sleeve 126 has welded or otherwise secured thereto a plurality of T-shaped supports 128. For the apparatus appearing in the drawing, it is preferable to employ twelve of the support members 128 arranged circumferentially of and in spaced relation to the sleeve 126. Each of the members 128 includes a base 128a which is secured to the ring 126 and which has right angle flanges 12% and 1280 forming the cross member of the T. To the cross members 12812 and 1280 is secured, as by bolts, or welding, the lower portion of the frusto-conical member 114.

To secure the frusto-conical member 114 and perforated ring 121 to the spaced support members 128, a plurality of spaced strips 130, as clearly appears in FIG. 3, are employed and which are secured, as by welding, to the member 114, ring 121 and members 128.

To further reinforce the conical member 114, a plurality of support members 132 are also employed. Twelve such support members are employed in the embodiment shown in FIGS 2 and 3. These support members 132 are secured, as by bolts 134, to the sleeve 126 and to the conical member 114 as by bolts 136.

Referring to FIG. 4 illustrating the details of the support members 132, it will be observed that each of the support members 132 includes an upright 138 and a cross bar 140 to which is secured the member 114. The sleeve 126, base 122, support members 128 and 132 provide lightweight yet rigid support means for the rotating means disposed in the chamber 102.

Adjacent its upper end, the chamber outer wall 106 carries .an annular flange 142 (FIGS. 2 and 5) to which is secured, as by bolts 144, a right angle ring 146 which has secured thereto, as by bolts 148, a depending sleeve ring 150 of elastomeric or like material.

Referring to FIG. 5, the frusto-co-nical member 114 carries at its upper end a generally cylindrical ring 152 in which is disposed the elastomeric ring 150. The ring 150 is so positioned that it contacts the front wall 154 of the ring 152 in sliding engagement therewith to prevent air, ice or vapor from flowing between the outer wall 106 and conical member 114 for purposes which will presently appear hereinafter.

In the practice of the present invention, a slurry of ice of the solvent is supplied through an inlet 156 into the chamber 102 and onto the inclined surface 116 of the member 114.

The ice flows downwardly along the inclined surface 116. Vapor introduced through the annular open end of the chamber 102 flows in contact with the ice on the surface 116 to condense the vapor and to melt the ice.

The condensate fluid of the vapor and fluid of the ice flows along the surface 116 and across the members and through the apertures 119 of the ring 121 into the space or chamber defined by the ring 121 and the sleeve 126. The members 128 are each ported, as indicated at 160, thereby providing communication between the compartments defined by the members 128, sleeve 126, bottom ring 122 and perforated ring 121. The sleeve 126 is. provided with a plurality of ports 162 (FIG. 2) which permit flow of the fluid into the bottom of the chamber 102. A discharge outlet 164 is provided in the outer wall 106 adjacent the bottom 108 of the chamber. Under normal operating conditions, it is preferable that the surface 168 of the pool of water 170 in the bottom of the chamber be located below the bottom of the drive ring 124 to prevent the Water from interfering with operation of the drive means for the ring 124.

T 0 remove air from the system, the bottom conical. member 122 is provided with a central opening 179. through which air may be discharged from the chamber 102. The air will flow, as shown by the arrows, through the outlet 179 into the chamber between the sleeve 126 and outer chamber wall 106 through the outlet 174. Thus, means are provided for removing air from the con densing chamber to minimize the quantity of air present in the chamber which would interfere with condensation of the vapor on the ice.

It will be appreciated that, as the rotatable means including the conical member 114 rotate, the ice supplied through the inlet 156 will distribute the ice on the inclined surface 116 of the member 114 in such a manner that the entire surface 116 is supplied with ice. Thus, the total surface area of the quantity of ice exposed to the evaporating conditions of the chamber 102 is enhanced. However, it will be appreciated that evaporation of the ice and condensation of the vapor is a function not only of the evaporative surface area but also of the time of residence of the ice in the chamber 102, means are preferably provided for delaying the movement of ice along the inclined surface 106 to thereby increase the residence time of any particular particle of ice in the chamber 102.

Such means, in the embodiment of the present invention shown in the drawing, comprise a spacer arrangement carrying horizontally disposed rods from which depend a plurality of spaced movable and pivotal plates 180 which have a plurality of perforations 181 to permit contact of vapor with the ice and drainage of the condensate fluid of the vapor and fluid of the ice from between the surface 116 and plates 180 (FIGS. 3 and 5).

Referring to FIGS. 2 and 3, the support arrangement comprises a plurality of horizontal members 182, 184 and 186 which are supported in such position from the ring 152, conical member 114 and perforated plate 121 respectively, and by a plurality of vertical members 188, 190 and 192 connected to members 182-186. These members may each be L-shaped in cross section (FIG. 4) and provide means for carrying a plurality of arcuate rods 196 (FIG. 3) in spaced relation to each other. From these rods are pivotally and laterally slideably carried the plurality of spaced plates 180 (FIG. 6).

As clearly appears in FIG. 3, twelve such support arrangements comprising the members 182-186 and 188- 192 are spaced around the surface 116 of the member 114.

In FIG. '7 is disclosed one method of connecting the rods 196 to the spacer members 188492 by threaded ends and nuts. It will be observed from FIG. 3 that the rods 196 are arcu-ate and extend around and in spaced relation to the surface 116.

In addition to the rods 196, the members 188, 190 and 192 carry depending plates 200, 202 and 204 which are apertured and which carry rods 206, 208 and 210 in the same plane as the rods 196 carried by the corresponding vertical support members 188-192 respectively. The rods 206-210 are arcuate and extend around the surface 116 in a manner similar to the rods 196. In FIG. 4, rods 208 are shown.

The plurality of individual plates 180 each includes a pair of turned ends 180a (FIG. 6) which are hooked over the rods 196 and the plates depend with the free end 180s located behind the corresponding lower rod 206, 208 or 210, as appears in FIG. 2 and FIG. 4. The end 1800' of each of the plates 180 is free to move towards and away from the rods 206-210 within the confines of said rods and the inclined surface 116. In this manner, if ice, as indicated at 220 in FIG. 2, should accumulate and move the plate 180 towards the rod 208, the rod 208 prevents further movement of the plate 180 inwardly toward the axis of the chamber 102 but permits a fluid formed by condensation of vapor of melting of the ice to flow between the edge or end 1800 and the wall surface 116 to the perforated plate 121.

Referring to FIG. 3, it will be observed that in one arrangement of plates 180, the outermost rod 196 located closest to the outer Wall 106 of the condensing chamber carries a pair of plates 180, the inner rod 196 carries a plurality of plates 180 and the rod 196 intermediate the inner and outer rods 196 carries a single plate 180. The plates are movable laterally towards and away from each other on the rods 196 as well as being pivotally mounted on the rods 196 and may be arranged to provide any number of patterns of arrangements, such as that appearing in FIG. 3, wherein the plates 180 are positioned relative to each other in such a manner as to limit the movement of ice in the most efiicient manner down along the surface 116 of the member 114.

Although FIG. 3 discloses only two portions of the surface 116 provided with a plurality of plates 180, it will be appreciated that any combination of plates 180 may be carried by the rods 196.

To cause rotation of the rotatable means, the ring 124 (FIG. 2) has a tape-red drive surface 250 which is disposed in a complementarily tapered groove 252 of drive means, generally indicated by the numeral 254 in FIG. 2. The drive means 254 includes a shaft 256 which is operably connected to the drive wheel 258. The shaft 256 is journaliled to a support 260 carried by the bottom 108 of the chamber 102. The drive wheel 258 is disposed 120 from a pair of similarly spaced idler wheels 262, one of which is shown in FIG. 2. The drive means 254 drive the ring 124 to cause rotation of the rotatable means including the member 114. The speed at which the ring is driven will depend upon such criteria as the feed rate of ice slurry to the chamber 102 and flow rate of vapor flowing to this chamber.

In operation, the evaporation apparatus is initiated to produce ice and vapor, the vapor being carried by the compressor into the open end of the chamber 102. After operation has been initiated, ice is washed in the counterwasher (not shown) and delivered to the inlet 156 and into the chamber 102. The drive means 254 are actuated at a suitable time, to cause rotation of the conical member 114. The ice then is distributed on the surface 116 and the plates 180 tend to control movement of ice on the surface by interrupting or delaying movement of ice of the ice slurry along the wall 116. Ice builds up behind the plates 180 and causes the plate ends 180c to move against the rods 206-210 which permits flow of fluid formed by condensing of the vapor in contact with the ice along the conical wall 116. The condensate fluid of the vapor and fluid of the ice flows downwardly along the inclined surface 116 and out through the perforations of the plate 121. Large size ice chunks are prevented from falling through the apertures of ring 121 by a screen ring (not shown) carried by the perforated ring 121. The fluid flows from the sleeve 126 through the apertures 162 to form the pool which, after normal operating conditions of the condensing chamber are established, has a level 168 above the outlet 164. The fresh water or potable water now flows or is discharged through the outlet 164 for further disposition or use.

Spaced from and above the air outlet 179 located in the bottom of the chamber is a guard plate 270 which is an annular ring carried by the inner wall 104. The plate 270 prevents ice from falling into the outlet 179. Ice which might accumulate on the top surface of the plate 270 tends to fall off and onto the bottom plate 122 rather than falling through the outlet 179. Air introduced into the chamber 102 will flow along with the water out the outlets 162 formed in the sleeve 126 and through the outlet 174. Similarly, air from the condensing chamber may flow through the inlet 179 and above the surface 168 of the .pool 170 to the outlet 174, thus minimizing the quantity of air collecting in the con densing chamber.

It will be appreciated that the members may be moved laterally to define various trap patterns for the ice.

Thus, there is provided with the present invention a new and improved condensing chamber apparatus for melting ice and condensing vapor which may include but a single fixed ice inlet, which includes rotatable means for receiving the ice to move the ice to an outlet, and includes means for introducing vapor into the chamber for contact with the ice to melt the ice and condense the vapor.

Although various minor modifications of the present invention will become readily apparent to those versed in the art, it should be understood that what is intended to be encompassed within the scope of the patent Warranted hereon are all such embodiments as reasonably and properly fall within the scope of the contribution to the art hereby made.

I claim:

1. Condensing chamber apparatus for condensing vapor and melting ice comprising: a condensing chamber, rotatable means including a surface inclined relative to the bottom of the chamber for receiving and moving ice, said surface being inclined to a degree sufficient to cause distribution on said surface of ice introduced into said chamber at least adjacent the area of introduction of said ice, means for rotating said rotatable means about a vertical axis, means including an inlet to said chamber for introducing ice into said chamber and onto said inclined surface, means for supplying vapor into Contact with said ice on said surface to condense the vapor and melt the ice, and means for removing condensate fluid of said vapor and fluid of said ice from said chamber.

2. Apparatus for condensing vapor and melting ice comprising: a condensing chamber, rotatable means in said chamber for receiving, distributing, and moving ice, said rotatable means including at least one surface receiving said ice while rotating to thereby distribute the ice on said surface at least adjacent the area of introduction of ice into said chamber, means for rotating said rotatable means about a vertical axis, means including an inlet to said chamber for introducing ice into said chamber and onto said rotatable means, means for supplying vapor into contact with ice on said rotatable means to condense the vapor and melt the ice, and means for removing condensate fluid of said vapor and fluid of said ice from said chamber.

3. Apparatus for condensing vapor and melting ice comprising: a condensing chamber, rotatable means including a member having a surface inclined inwardly and downwardly towards the bottom of the chamber, said surface being inclined to a degree sufiicient to cause distribution on said surface of ice introduced into said chamber ontosaid surface at least adjacent the area of introduction of said ice, said surface being adapted to receive and to move ice from the upper end thereof to the bottom of said chamber, means for rotating said rotatable means about a vertical axis, means including an inlet to said chamber for introducing ice onto said inclined surface adjacent the upper end thereof, means for supplying vapor into contact with ice on said surface to condense the vapor and to melt the ice, and means for removing condensate fluid of said vapor and fluid of said ice from said chamber.

4. The apparatus of claim 3 wherein said rotatable member is a hollow frusto-conical member and said inclined surface is the inner annular surface of said conical member.

5. Apparatus for condensing vapor and melting ice comprising: a condensing chamber, a hollow frusto-conical member rotatably mounted in said chamber having a bottom Opening of lesser diameter than the top opening thereof and defining an ice receiving chamber, means for supplying ice adjacent the upper end of the frusto-conical member while said member rotates, means for rotating said member about a vertical axis, an inlet to said chamber for introducing vapor into contact with ice on said surface to condense the vapor and to melt the ice, and means for removing condensate fluid of the vapor and fluid of the ice from the ice receiving chamber of said member.

6.. The apparatus of claim 5 wherein said member is spaced from the walls of said condensing chamber.

7. The apparatus of claim 5- wherein said member is axially aligned with said condensing chamber.

8. Apparatus according to claim 7 including means responsive to ice accumulation on said surface for temporarily delaying movement of ice downwardly along said inclined surface.

9. Apparatus according to claim 8 wherein said means for temporarily delaying movement of ice along said inclined surface includes movable members located at preselected positions on said inclined surface.

10. The apparatus of claim 8 wherein said last mentioned means includes a plurality of spacer members carried by said inclined surface, and a plurality of movable sheet members, at least two of which have perforations therein, depending from said spacer members with one end of each member located in the path of ice moving along said surface whereby said sheet members temporarily interrupt movement of ice along said surface.

11. Apparatus according to claim 10 wherein said sheet members are movable laterally along rods carried by said spacer members.

12. Apparatus according to claim 11 wherein said sheet members are pivoted about said rods.

13. Apparatus according to claim 5 wherein said means for rotating said rotatable means comprises a ring carried by said rotatable means and drive means for rotating said ring about the vertical axis of said chamber.

14. Apparatus for condensing vapor and melting ice comprising: a condensing chamber, rotatable means including a surface inclined relative to the bottom of the chamber for receiving and moving ice to the bottom of said chamber, said surface being inclined to a degree sufiicient to cause distribution on said surface of ice introduced into said chamber at least adjacent the area of introduction of said ice, means for rotating said rotatable means about a vertical aXis, means carried by said rotatable means for temporarily interrupting movement of ice downwardly along said surface, means including an inlet to said chamber for introducing ice into said chamber and onto said inclined surface, means for supplying vapor into contact with ice on said surface to condense the vapor and to melt the ice, and means for removing condensate fluid of said vapor and fluid of said ice from said chamber.

15. Apparatus according to claim 14 including means for maintaining vacuum conditions in said chamber and wherein said means for temporarily interrupting movement of ice includes a plurality of members located at preselected positions on said inclined surface.

16. The apparatus of claim 14 wherein said means for temporarily interrupting movement of ice includes a plurality of spacer members carried by said inclined surface, and a plurality of perforated sheet members movably depending from one end of each sheet member, said spacer members located in the path of ice moving along said surface whereby said sheet members temporarily interrupt movement of ice along said surface.

17. Apparatus according to claim 16 wherein said sheet members are movable laterally along rods carried by said spacer members.

18. Apparatus according to claim 17 wherein said sheet members are pivoted about said rods.

19. The apparatus of claim 16 wherein said inlet for introducing ice is a single inlet.

20. The apparatus of claim 19 wherein said inlet is located for tangentially introducing ice onto said rotatable means.

21. A distribution method of condensing vapor and melting ice comprising: providing a chamber having an inlet, supplying ice through said inlet to a surface in said chamber and inclined to a degree suificient to cause distribution of ice on said surface as it is introduced into the chamber at least adjacent the area of introduction of the ice, rotating said inclined surface about a vertical axis while supplying ice through said inlet to thereby distribute the ice, and supplying vapor into contact with the ice on said rotating surface to thereby condense the vapor and melt the ice.

22. The method of claim 21 including the step of temporarily interrupting movement of ice downwardly on said surface.

References Cited by the Examiner UNITED STATES PATENTS 433,339 7/1890 Forbes 210210 933,837 9/1909 DHomergue 126343.5 X 1,073,427 9/1913 Lapsley 126343.5 1,360,238 11/1920 McGill 126-3435 3,011,493 12/1961 Zieba 126343.5 3,103,792 9/1963 Davids 62-67 X 3,121,626 2/1964 Zarchin 62124 X OTHER REFERENCES German application 1,125,405, Klencke, printed March 15, 1962 (K39801 IVc/12a), 3 pages spec.; 3 sheets drawings.

FREDERICK L. MATTESON, JR., Primary Examiner.

JAMES W. WESTHAVER, Examiner. 

1. CONDENSING CHAMBER APPARATUS FOR CONDENSING VAPOR AND MELTING ICE COMPRISING: A CONDENSING CHAMBER, ROTATABLE MEANS INCLUDING A SURFACE INCLINED RELATIVE TO THE BOTTOM OF THE CHAMBER FOR RECEIVING AND MOVING ICE, SAID SURFACE BEING INCLINED TO A DEGREE SUFFICIENT TO CAUSE DISTRIBUTION ON SAID SURFACE OF ICE INTRODUCED INTO SAID CHAMBER AT LEAST ADJACENT THE AREA OF INTRODUCTION OF SAID ICE, MEANS FOR ROTATING SAID ROTATABLE MEANS ABOUT A VERTICAL AXIS, MEANS INCLUDING AN INLET TO SAID CHAMBER FOR INTRODUCING ICE INTO SAID CHAMBER AND ONTO SAID INCLINED SURFACE, MEANS FOR SUPPLYING VAPOR INTO CONTACT WITH SAID ICE ONE SAID SURFACE TO CONDENSE THE VAPOR AND MELT THE ICE, AND MEANS FOR REMOVING CONDENSATE FLUID OF SAID VAPOR AND FLUID OF SAID ICE FROM SAID CHAMBER. 